CN1871440A - Drive mechanism - Google Patents

Drive mechanism Download PDF

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Publication number
CN1871440A
CN1871440A CNA2004800314906A CN200480031490A CN1871440A CN 1871440 A CN1871440 A CN 1871440A CN A2004800314906 A CNA2004800314906 A CN A2004800314906A CN 200480031490 A CN200480031490 A CN 200480031490A CN 1871440 A CN1871440 A CN 1871440A
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CN
China
Prior art keywords
transmission device
piston
pressure
primary
cylinder chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CNA2004800314906A
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Chinese (zh)
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CN1871440B (en
Inventor
约尔格·丹托格雷贝尔
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of CN1871440A publication Critical patent/CN1871440A/en
Application granted granted Critical
Publication of CN1871440B publication Critical patent/CN1871440B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • B26D5/12—Fluid-pressure means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
    • B29C45/17—Component parts, details or accessories; Auxiliary operations
    • B29C45/76—Measuring, controlling or regulating
    • B29C45/82—Hydraulic or pneumatic circuits
    • B29C2045/824—Accumulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
    • B29C45/17—Component parts, details or accessories; Auxiliary operations
    • B29C45/76—Measuring, controlling or regulating
    • B29C45/82—Hydraulic or pneumatic circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member

Abstract

Disclosed is a drive mechanism, particularly for punching machines and nibbling machines, comprising a hydraulic force transmitting element (4) and a spindle drive (26) for driving the force transmitting element. A biasing mechanism (8) is provided for biasing the force transmitting element (4).

Description

Transmission device
Technical field
The present invention relates to a kind of transmission device of the preamble according to claim 1.
Background technique
Dynamo-electric hydraulic transmission like this is applied in some working machines, can realize adjustment movement and very big power fast in these working machines.Preferred working machine is punch press, nibbling machine, press and plastic-injection moulding machine.
A kind of transmission device that is used for plastic-injection moulding machine is disclosed in the applicant's DE 101 35 516 A1.This transmission device has a hydraulic coupling transducer, and the latter is connected by the hydraulic regulating device of high pressure pipe line with shaping crushing plate (Formspannplatte).This force transducer has a primary piston piston-cylinder unit and secondary piston cylinder units that has little primary piston and big secondary piston.These two piston cylinder units are provided with mutually nestedly, and wherein primary piston is operated by the main shaft driving device of an electricity and therefore can be operated the shaping crushing plate.In order to regulate the zero-bit of transmission device, for example owing to leak, the backstop of described shaping crushing plate resistance machinery runs in the position of opening fully.Then, raise by valve that pressure medium between controlling device and the force transducer connects and secondary piston run to the corresponding position of the open position of moulding crushing plate in.After regulating zero-bit, described valve can enter into its closed position again and can begin new work cycle.
The shortcoming of described known solution is that the adjusting of zero-bit expends time in very much.In addition, the shortcoming that also has is to realize the high strength of punch press or the desired transmission device of nibbling machine by known force transducer.
Summary of the invention
Task of the present invention provides a kind of transmission device of eliminating above-mentioned shortcoming.
Described task solves by a kind of transmission device with characteristic of claim 1.
Transmission device according to the present invention has force transducer and main shaft driving device.Described force transducer has primary unit and secondary units, and they have a stepped piston respectively.These unit are set in this wise, make the big significant surface of these pistons form the border of cylinder chamber jointly and the less significant surface of these pistons forms the border of doughnut respectively, wherein these doughnuts form the connection of hydraulic pressure mutually.Primary piston can drive by main shaft driving device.Secondary piston acts on workpiece directly or indirectly.According to the present invention, be provided with the pre-load means that is used for pre-loaded pressure is imposed on the cylinder chamber.
Advantage according to transmission device of the present invention is, it has high strength, and to set up on the direction efficient pressure in power poor because improve by preload.
Pre-load means can open and close by back pressure valve.Pre-load means can be pump and/or hydraulic energy storage device.Can use suction booster in order to supply with hydraulic energy storage device, the latter is for example driven by secondary units, makes pressure medium being supplied and can be loaded to described hydraulic energy storage device from fuel tank.Advantageously, described suction booster is configured to have the plunger pump of trunk piston, and wherein the pressure on the secondary piston rests on the trunk piston by spring, makes suction booster not reload hydraulic energy storage device from a ultimate pressure.Water can be used as pressure medium.
The doughnut of primary piston unit forms hydraulic pressure with the doughnut of secondary piston unit by high pressure pipe line and is connected.In described high pressure pipe line, be provided for the modulating valve that the described hydraulic pressure of mediation throttling connects according to embodiments of the invention.Described modulating valve enters closed position and therefore fixed secondary piston hydraulically when regulating the zero-bit of transmission device, and modulating valve can also enter run through the position and therefore secondary piston can move.In order to determine correct zero-bit of regulating and can to readjust zero-bit in order to determine whether, displacement measurement system and/or pressure-measuring system are set, and described these measuring systems detect the mutual spacing of these two stepped pistons and/or at first detect pressure in the cylinder chamber.
In addition, the doughnut of primary unit is connected with cylinder chamber formation hydraulic pressure.Described connection can be passed through valve equally, is called delivery valve below and goes up the mediation throttling.Therefore pressure medium can be discharged to another chamber and primary piston from one of them chamber and for example arrive zero-bit when secondary piston is static.
In order to improve the power of the secondary piston that directly or indirectly imposes on workpiece, a plurality of primary units can synchronous working.In the case, a main shaft driving device disposes respectively to a primary unit or a main shaft driving device and drives a plurality of screw rods by uni-drive gear box.Primary piston a plurality of basically, separate existence has such advantage, and promptly the single engaging position of the screw rod/bolt and nut that is connected with primary piston can be changed and therefore can prolong the working life of screw rod.
In order to obtain transmission device compact structure form as far as possible, the cylinder block housing of primary unit can be surrounded by the cylinder block housing of secondary units.If primary unit surrounds by the secondary piston end at least, can also construct such structural type more compactly.
Some other favourable form of implementation is the object of other dependent claims.
Description of drawings
Describe more preferred forms of implementation of the present invention in detail below with reference to schematic accompanying drawing.
Accompanying drawing is represented:
Fig. 1 illustrates the transmission device that has the hydraulic energy storage device that is used for preload according to of the present invention; And
Fig. 2 illustrates the force transducer with the primary unit in the secondary units of being received in.
Embodiment
Fig. 1 illustrates one preferably according to transmission device 2 of the present invention, and in particular for the transmission device of transmission punch press or nibbling machine, it has force transducer 4, main shaft driving device 6 and is used for the pre-load means 8 of the preload of force transducer 4.
Force transducer 4 has primary unit 10 and secondary units 12.These two unit 10,12 have one respectively and are received in the cylinder block housing 18,20 and primary piston or secondary piston 14,16 that be configured to stepped piston.Piston 14,16 has a piston rod 22,24 respectively, and they are from the distolateral cylinder block housing 18,20 that runs through.Effect screw rod 26 on the piston rod 22 of primary unit 10, the latter forms effectively engagement with the bolt and nut 68 of the main shaft driving device 6 that is used for driving force transducer 4.The piston 24 of secondary units 12 for example can with a pending workpiece (not shown) directly or indirectly by putting, make it to apply a big power to workpiece.
For the mutual spacing of definite these two pistons 14,16 and/or in order to measure the pressure in the cylinder chamber 32, be provided with displacement measurement system and/or pressure-measuring system (not shown).By measured spacing and/or pressure, can determine the variation of relative position of piston 14,16 and/or the variation of the pressure in the cylinder chamber 32, so can detect the possible phase mutual deviation of piston 14,16.For example, flow in the cylinder chambers 32 by piston 14,16 from the doughnut 38,40 that has applied high pressure at the internal pressure medium owing to the phase mutual deviation that occurs piston 14,16 to internal leakage.In addition, can regulate by the zero-bit that the relative spacing of two pistons 14,16 being detected by displacement measurement system is carried out transmission device 2 simply.When the common function of the illustrated embodiment of transmission device 2 according to the present invention explanation, describe in detail and regulate zero-bit.
In form of implementation according to Fig. 1, a primary unit 10 only is set, but also can secondary piston 16 of a plurality of primary unit 10 effects.If a plurality of primary units 10 are set, then each primary unit 10 can dispose oneself a main shaft driving device 6.Main shaft driving device 6 of the interchangeable scheme of another one regulation is used for all primary units 10, and the latter for example effectively is connected with single primary piston 14 formation by a uni-drive gear box.A plurality of primary piston 14 that act on secondary piston 16 have such advantage, and promptly single screw rod 26 can be changed with the engaging position of the bolt and nut 68 of main shaft driving device 6.Promptly for example, secondary piston 16 is reduced by operation axis drive unit 6 with the spacing of primary piston 14, and correspondingly increases the spacing of second primary piston, so that alternately engagement or the loading and can use screw flight 26 in the same manner of screw rod section.
Piston 14,16 has a bigger significant surface and a less significant surface 28,30,34,36 respectively.Bigger significant surface 28,30 forms the border of cylinder chambers 32 and less significant surface 34,36 forms the border of doughnut 38,40 respectively.Extend piston rod 22,24 from less significant surface 34,36, so less significant surface 34,36 reduces the cross-section area of piston rod 22,24 approximately separately with respect to bigger significant surface.
Doughnut 38,40 forms the connections of hydraulic pressure mutually by high pressure pipe line 42, wherein in order to interrupt described connection, is provided with in high pressure pipe line 42 and has a modulating valve 44 that runs through a position and a closed position.
Cylinder chamber 32 forms hydraulic pressure by cylinder tube 46 with the doughnut 38 of primary unit 10 and is connected.For throttling and raise described be connected also to be provided with in the cylinder tube 46 have a back pressure valve 48 that runs through a position and a closed position.
The pre-load means 8 of force transducer 4 is a hydraulic energy storage device 50 in an illustrated embodiment.Described hydraulic energy storage device is connected by storage tube 52 and cylinder chamber 32 formation hydraulic pressure, wherein is connected to be provided with in the storage tube 52 and has a back pressure valve 54 that runs through a position and a closed position in order to set up or to interrupt described hydraulic pressure.
To appear at piston rod 22,24 and run through the outside leakage in cylinder block housing 18,20 there in order to compensate, be provided with suction booster 56, it is delivered into pressure medium hydraulic system and therefore loads hydraulic energy storage device 50 from fuel tank T by the tank tube 62 that inserts storage tube 52.Suction booster 56 preferable configuration are the plunger pump with trunk piston 58, and wherein said plunger pump and secondary piston 16 forms machineries or hydraulic pressure effectively is connected and comes transmission and pressure medium to be transported in the described hydraulic system according to their stroke.The spring 60 that moves through of secondary piston 16 is delivered to trunk piston 58.The elasticity rate of the described spring of design makes that only a power can be transferred to trunk piston 58 like this, and described power equates with the maximum pressure boost of hydraulic energy storage device 50.When surpassing described power, spring 60 is compressed, so that does not occur the pressure increase on hydraulic energy storage device 50.For fear of on suction booster 56 directions or, in tank tube 62 and a safety check 64,66 directly is set respectively before fuel tank T in the backflow of fuel tank T direction upward pressure medium.
The following describes function according to transmission device 2 of the present invention.Function and work cycle are divided into preload basically, supply with secondary piston 16, punching press and secondary piston 16 return-to-home positions from original position.After the several work cycle, be used to regulate the zero-bit adjusting of original position according to leakage loss.
In order to begin a work cycle, transmission device 2 is positioned at original position.In this position, piston 14,16 is adjusted to defined mutual spacing.Transmission device 2 is adjusted in its zero-bit.
Transmission device 2 is pre-loaded in the described original position according to the present invention.In the case, open modulating valve 44 and back pressure valve 54 and close delivery valve 48.By opening modulating valve 44, these two doughnuts 38,40 form mutually and connect, so that pressure balance occurs between these chambers 38,40.By hydraulic energy storage device 50, a pre-loaded pressure is imposed on cylinder chamber 32, the latter rests on the big significant surface 30 than big significant surface 18 and secondary piston 16 of primary piston 14.But because the bolt and nut 68 effective engages fixed of primary piston 14 by screw rod 26 and main shaft driving device 6 in its position and so do not increase the volume of doughnut 38 yet, secondary piston 16 can not shift out from its present position.Therefore, set up pre-loaded pressure in the cylinder chamber 32 by hydraulic energy storage device 50.As long as corresponding pre-loaded pressure in cylinder chamber 32, occurs, just close back pressure valve 54 and block hydraulic energy storage device 50 with respect to cylinder chamber 32.
When after preload, supplying with, secondary piston 16 indirectly or directly with pending workpiece by putting.Close delivery valve 48 and back pressure valve 54 and open modulating valve 44.Controlled and the screw rod 26 of main shaft driving device 6 carries out rotational motion, so that primary piston 14 is sailed into.Secondary piston 16 is rolled away from corresponding to primary piston 14 and pressure medium is discharged to the doughnut 38 of primary unit 10 by high pressure pipe line 42 from the doughnut 40 of secondary units 12.The volume ratio of doughnut 38,40 is selected in this wise, and promptly the volume of the doughnut 38 of primary unit 10 increases with the volume of the doughnut 40 of secondary units 12 and reduces to equate the direction decline towards workpiece of level piston 16.
When punching press, extrude that piston 48 and back pressure valve 54 keep closing and modulating valve 44 stays open.Control main shaft driving device 6 and screw rod 26 carry out rotational motion, and rotational motion makes primary piston 14 continue to sail into.But, because secondary piston 16 when supplying with directly or indirectly with pending workpiece by putting, so obstruction secondary piston 16 is rolled away from immediately.Therefore, be arranged in the pressure medium of cylinder chamber 32,, just be compressed as long as it allows compression.Cylinder chamber 32 correspondingly reduces and doughnut 38 increases of primary unit, and the pressure so the rising of the pressure in the cylinder chamber 32 surpasses pre-loaded pressure in the doughnut 38,40 descends.Therefore, applying efficient pressure difference rising on the direction of stamping press.The pressure of determining from cylinder chamber 32, secondary piston 16 can increase the power essential to punching press.Described stamping press is set up soon by preload, so high-intensity stamping process occurs having.After the punching press and after secondary piston 16 rolls away from, pre-loaded pressure appears again in cylinder chamber 32.
When turning back to its original position in order to implement new work cycle secondary piston 16, delivery valve 48 and back pressure valve 54 are in closed position and open modulating valve 44.Main shaft driving device 6 is controlled in this wise, makes screw rod 26 carry out reverse rotational motion, and wherein primary piston 14 is rolled away from.The doughnut 38 of primary unit 10 diminishes and pressure medium is discharged in the doughnut 40 of secondary units 12 by modulating valve 44.Doughnut 40 correspondingly increases and secondary piston 16 is moved along the direction of sailing into.In the case, secondary piston 16 is owing to primary piston 14 returns rapidly in the outgoing position that is transported to it, so can begin a new work cycle rapidly.
According to the relative position of these two pistons 14,16 and/or appear at pressure in the cylinder chamber 32, after several work cycle, carry out the adjusting of the zero-bit of transmission device 2.In the case, piston 14,16 is introduced into again in their definite mutually relative positions.Owing to leak the change of the mutual relative position of at first regulating two pistons 14,16 and/or the change of the pressure in the cylinder chamber 32.
Because inside and outside leakage may be leaked.Pressure medium infiltrates cylinder chamber 32 from doughnut 38,40 by piston 14,16 when internal leakage.When externally leaking, the pressure medium in piston cylinder 22,24 zones outwards is exuded in the external environment condition 84 from doughnut 38,40.
Basically because the pressure ratio cylinder chamber 32 higher generation internal leakages of doughnut 38,40 medium or to the leakage of inside.Inside leakage is because the pressure medium that flows out from doughnut 38,40 causes reducing of doughnut 40 and the increase and therefore secondary piston 16 declines of cylinder chamber 32.In addition, the pressure in the cylinder chamber 32 descends.But, because according to preload of the present invention, the pressure in the cylinder chamber 32 is brought up to so high level, promptly can not form low pressure in cylinder chamber 32.
By pressure medium being discharged on the external environment condition 84 when the external leakage, from whole hydraulic system, extract pressure medium out, because the pressure in this system descends.Up to a definite pressure medium amount, the pressure medium loss can be by hydraulic energy storage device 50 compensation.But for pressure being remained on chronically a constant level, can in a stroke of secondary piston 16, from fuel tank T, be transported in the hydraulic system pressure medium and be loaded by suction booster 56 to hydraulic pressure accumulator 50.
In order to occur regulating zero-bit behind the phase mutual deviation, modulating valve 44 and back pressure valve 54 are in closed position and open delivery valve 48.By the closed position of modulating valve 44, doughnut 38,40 is spaced from each other, so pressure medium can not flow into the doughnut 38 of primary unit 10 from the doughnut 40 of secondary units 12.Secondary piston 16 hydraulically is fixed in its position.By displacement measurement system, detect these two pistons, 14,16 present mutual spacing and main shaft driving devices and controlled in this wise, make to be adjusted on the predetermined position between the piston 14,16.Owing to open delivery valve 48, setting up the doughnut 38 of primary unit 10 is connected with pressure medium between the cylinder chamber 32, so when moving on the direction of secondary piston 16 in order to reduce spacing primary piston 14, pressure medium can be discharged into the doughnut 38 from cylinder chamber 32.Therefore opposite with known solution, be no longer necessary for zero-bit adjusting secondary piston 16 according to the present invention and be driven out to open position with expending time in.Zero-bit adjusting according to the present invention is approximate can be implemented rapidly and simply at any time.As long as be adjusted to the predetermined distance between these two pistons 14,16 again, transmission device 2 is located in its definite zero-bit or original position, so can begin new work cycle in case of necessity after the repetition preload of system.Quick zero-bit is like this regulated and can be implemented by pressure-measuring system equally.Under these circumstances, the pressure in the cylinder chamber 32 measured and with authorized pressure relatively.
Fig. 2 illustrates the force transducer 4 with the primary unit 10 that is surrounded by secondary units 12.Such mode of structure has been characterised in that good compactedness owing to reduce the axial length of force transducer 4.
Secondary piston 16 has gap 70, and the latter extends in its piston rod 24 promptly has the end section of very little external diameter in the zone of bigger significant surface 30 and in described form of implementation.Primary unit 10 extend in the described gap 70 by the end section 72 of its cylinder block housing 18.By its second end section 88 of cylinder block housing 18, primary unit 10 is fixed on the base plate 86 of cylinder block housing 20 of secondary units 12.The cylinder block housing 18 of primary unit 10 is away from inner region 74 and away from the base plate 76 in gap 70, so the cylinder chamber 78 of setting up primary unit 10 by annular space 82 is connected with hydraulic pressure between the cylinder chamber 80 of secondary units and therefore same pressure is applied to this two pistons 14, on 16 the bigger significant surface 28,30.These two cylinder chambers 78,80 are identical according to the cylinder chamber 32 of the form of implementation of Fig. 1 with the front.The doughnut 38,40 of primary unit 10 and secondary units 12 is axially limited out the border and forms hydraulic pressure mutually by high pressure pipe line 42 by less significant surface 34,36 and connects.Corresponding to the front form of implementation illustrated, in described high pressure pipe line 42, be provided with the valve (not shown) that is used for the pressure medium connection between the mediation restrictor ring shape chamber 38,40 according to Fig. 1.
Function is identical according to the illustrated embodiment of Fig. 1 with the front, so omit explanation again.
Disclose a kind of transmission device, in particular for the transmission device of punch press and nibbling machine, it has the hydraulic coupling transducer and is used for the main shaft driving device of driving force transducer, wherein is provided with the pre-load means that is used for the preload force transducer.
Reference numeral
2 transmission devices
4 force transducers
6 main shaft driving devices
8 pre-load means
10 primary units
12 secondary units
14 primary piston
16 secondary piston
18 gas cylinder block housing housings
20 gas cylinder block housing housings
22 piston rods
24 piston rods
26 screw rods
28 bigger significant surfaces
30 bigger significant surfaces
Cylinder chambers 32
34 less significant surfaces
36 less significant surfaces
38 doughnuts
40 doughnuts
42 high pressure pipe lines
44 modulating valve
46 cylinder tubes
48 delivery valves
50 hydraulic energy storage devices
52 storage tubes
54 back pressure valves
56 suction boosters
58 trunk pistons
60 springs
62 tank tubes
64 safety check
66 safety check
68 bolt and nuts
70 gaps
72 end section
74 inner regions
76 base plates
Cylinder chambers 78
Cylinder chambers 80
82 annular spaces
84 external environment conditions
86 base plates
88 end section

Claims (12)

1. transmission device, transmission device in particular for punch press and nibbling machine, described transmission device has hydraulic coupling transducer (4) and is used to drive the main shaft driving device (6) of primary piston, described hydraulic coupling transducer has primary unit (10) and secondary units (12), these two unit structures are stepped piston (14,16) and their bigger significant surfaces (28,30) form the border of cylinder chamber (32) jointly and their less significant surfaces (34,36) form doughnut (38 respectively, 40) border, these doughnuts (38 wherein, 40) hydraulically be connected, wherein secondary piston (16) acts on the workpiece to be loaded directly or indirectly, it is characterized in that, is used for pre-loaded pressure is imposed on the pre-load means (8) of cylinder chamber (32).
2. transmission device according to claim 1 is characterized in that, described pre-load means (8) can be passed through back pressure valve (54) and open and close.
3. transmission device according to claim 1 and 2, it is characterized in that, described two doughnuts (38,40) form hydraulic pressure mutually by high pressure pipe line (42) and connect, and wherein are provided with to be used for the modulating valve (44) that the described hydraulic pressure of mediation throttling connects in described high pressure pipe line.
4. according to one of them described transmission device of claim 1 to 3, it is characterized in that, be provided with the displacement measurement system and/or the pressure-measuring system that are used for the mutual relative position of detection of primary piston and secondary piston (14,16) and/or are used for detecting the pressure of cylinder chamber (32).
5. require one of them described transmission device according to aforesaid right, it is characterized in that, described cylinder chamber (32) hydraulically is connected with the doughnut (38) of primary unit (10), wherein is provided with delivery valve (48) for the described hydraulic pressure of last mediation throttling connects.
6. require one of them described transmission device according to aforesaid right, it is characterized in that, described pre-load means (8) is hydraulic energy storage device (50) or pump.
7. require one of them described transmission device according to aforesaid right, it is characterized in that, be provided with the suction booster (56) that is used to supply with hydraulic energy storage device (50), described suction booster can be driven by secondary piston (16).
8. transmission device according to claim 7 is characterized in that, the pressure on the secondary piston (16) by spring action on the trunk piston (58) of suction booster (56).
9. require one of them described transmission device according to aforesaid right, it is characterized in that, the parallel connection of a plurality of screw rods (26).
10. require one of them described transmission device according to aforesaid right, it is characterized in that, the cylinder block housing (18) of described primary unit (10) is surrounded by the cylinder block housing (20) of described secondary units (12).
11. transmission device according to claim 10 is characterized in that, an end section (72) of the cylinder block housing (18) of described primary unit (10) immerses in the gap (70) of described secondary piston (16).
12. require one of them described transmission device, it is characterized in that pressure medium is a water according to aforesaid right.
CN2004800314906A 2003-11-25 2004-11-10 Drive mechanism Expired - Fee Related CN1871440B (en)

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DE10354952.8 2003-11-25
DE10354952A DE10354952A1 (en) 2003-11-25 2003-11-25 driving device
PCT/DE2004/002485 WO2005052382A1 (en) 2003-11-25 2004-11-10 Drive mechanism

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CN1871440A true CN1871440A (en) 2006-11-29
CN1871440B CN1871440B (en) 2010-06-30

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US (1) US7555901B2 (en)
EP (1) EP1706648B1 (en)
CN (1) CN1871440B (en)
AT (1) ATE393316T1 (en)
DE (2) DE10354952A1 (en)
WO (1) WO2005052382A1 (en)

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CN103851037A (en) * 2012-11-29 2014-06-11 何荣志 Multi-pressure source energy-saving hydraulic pressure station
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Also Published As

Publication number Publication date
DE10354952A1 (en) 2005-06-30
EP1706648A1 (en) 2006-10-04
US7555901B2 (en) 2009-07-07
CN1871440B (en) 2010-06-30
DE502004006966D1 (en) 2008-06-05
EP1706648B1 (en) 2008-04-23
ATE393316T1 (en) 2008-05-15
WO2005052382A1 (en) 2005-06-09
US20070084357A1 (en) 2007-04-19

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